Accumulator check systems and methods

ABSTRACT

A system includes: a state module configured to selectively set a present state to a first state; a valve control module configured to determine first target open and closed states for valves of a suspension system based on the present state and to open and close the valves of the suspension system according to the first target open and closed states, respectively; a pump control module configured to, when the valves are in the first target open and closed states, respectively, selectively operate an electric pump of the suspension system in a first direction and increase a pressure of hydraulic fluid in a first portion of the suspension system including an accumulator, where the valve control module is configured to decrease the pressure in the first portion after the increase; and a diagnosis module configured to selectively diagnose a fault in the accumulator based on a pressure during the decrease.

FIELD

The present disclosure relates to suspension systems and more particularly to systems and methods for checking accumulators of suspension systems.

BACKGROUND

The background description provided here is for the purpose of generally presenting the context of the disclosure. Work of the presently named inventors, to the extent it is described in this background section, as well as aspects of the description that may not otherwise qualify as prior art at the time of filing, are neither expressly nor impliedly admitted as prior art against the present disclosure.

Suspension systems improve the ride of a vehicle by absorbing bumps and vibrations that would otherwise unsettle the vehicle body. Suspension systems also improve safety and control by improving contact between the ground and the tires of the vehicle. One drawback of suspension systems is that basic spring/damper arrangements will allow the vehicle to roll/lean right or left during corning (e.g., in turns), pitch forward under deceleration (e.g., under braking), and pitch back under acceleration. The lateral acceleration the vehicle experiences in turns causes a roll moment where the vehicle will lean/squat to the right when turning left and to the left when turning right. The fore and aft acceleration the vehicle experiences under acceleration and braking causes a pitch moment where the vehicle will lean forward loading the front axle during braking and aft, loading the rear axle, under acceleration. These roll and pitch moments decrease grip, cornering performance, and braking performance and can also be uncomfortable to the driver and passengers. Many vehicles are equipped with stabilizer bars/anti-roll bars, which are mechanical systems that help counteract the roll and/or pitch moments experienced during driving. For example, anti-roll bars are typically mechanical linkages that extend laterally across the width of the vehicle between the right and left dampers. When one of the dampers extends, the anti-roll bar applies a force to the opposite damper that counteracts the roll moment of the vehicle and helps to correct the roll angle to provide flatter cornering. However, there are several drawbacks associated with these mechanical systems. First, there are often packaging constraints associated with mechanical systems because a stabilizer bar/anti-roll bar requires a relatively straight, unobstructed path across the vehicle between the dampers. Second, stabilizer bars/anti-roll bars are reactive and work when the suspension starts moving (i.e. leaning). Such mechanical systems cannot be easily switched off or cancelled out when roll stiffness is not need. Some vehicles do have stabilizer bar/anti-roll bar disconnects that may be manually or electronically actuated, but the complexity and cost associated with these systems may make them ill-suited for most vehicle applications.

In an effort to augment or replace traditional mechanical stabilizer bars/anti-roll bars, anti-roll suspension systems are being developed that hydraulically connect two or more dampers in a hydraulic circuit where the extension of one damper produces a pressure change in the other damper(s) in the hydraulic circuit that makes it more difficult to compress the other damper(s) in the hydraulic circuit. This pressure change in the other damper(s) increases the roll stiffness of the suspension system of the vehicle. However, the downside of such systems is that ride comfort is more difficult to achieve because bump forces can be transmitted from one damper to another damper across the hydraulic circuit resulting in unwanted suspension movement. Accordingly, there remains a need for improved vehicle suspension systems that can minimize pitch and roll while maintaining acceptable levels of ride comfort.

A suspension system may include multiple accumulators. The accumulators may be filled with a predetermined amount of fluid set according to one or more design considerations. Improper accumulator pressures may decrease suspension system performance. There is therefore a need to accurately check and control the accumulator pressures before use and how much hydraulic fluid is within each accumulator.

SUMMARY

In a feature, an accumulator checking system for a suspension system of a vehicle includes: a state module configured to selectively set a present state of an accumulator check for the suspension system to a first state; a valve control module configured to determine first target open and closed states for valves of the suspension system based on the present state being set to the first state and to open and close the valves of the suspension system according to the first target open and closed states, respectively; a pump control module configured to, when the valves are in the first target open and closed states, respectively, selectively operate an electric pump of the suspension system in a first direction and increase a pressure of hydraulic fluid in a first portion of the suspension system including an accumulator, where the valve control module is configured to selectively open one or more of the valves to decrease the pressure in the first portion after the increase; and a diagnosis module configured to: selectively record the pressure in the first portion based on a second derivative of the pressure while the pressure is decreasing; and selectively diagnose a fault in the accumulator based on the recorded pressure.

In further features, the diagnosis module is configured to record the pressure in the first portion when the second derivative of the pressure is greater than a predetermined value.

In further features, the diagnosis module is configured to determine the second derivative of the pressure in the first portion.

In further features, the diagnosis module is configured to determine the second derivative of the pressure using a Savitzky Golay filter.

In further features, the diagnosis module is configured to diagnose the fault in the accumulator when the recorded pressure is less than a predetermined pressure.

In further features, the diagnosis module is configured to selectively diagnose that no fault is present in the accumulator when the recorded pressure is greater than the predetermined pressure.

In further features, the diagnosis module is further configured to: determine a total volume of hydraulic fluid input to the first portion of the suspension system while the pump control module operated the electric pump in the first direction and increased the pressure from a first predetermined pressure to a second predetermined pressure; and selectively diagnose the fault in the accumulator further based on the total volume of hydraulic fluid input.

In further features, the diagnosis module is configured to diagnose the fault when the total volume of hydraulic fluid input to the first portion is less than a predetermined volume.

In further features, the diagnosis module is configured to diagnose that no fault is present in the accumulator when the total volume of hydraulic fluid input to the first portion is greater than the predetermined volume.

In further features: the state module is configured to selectively set the present state of the accumulator check for the suspension system to a second state; the valve control module is configured to determine second target open and closed states for the valves of the suspension system based on the present state being set to the second state and to open and close the valves of the suspension system according to the second target open and closed states, respectively; the pump control module is configured to, when the valves are in the second target open and closed states, respectively, selectively operate the electric pump of the suspension system in the first direction and increase a second pressure of hydraulic fluid in a second portion of the suspension system including a second accumulator, the valve control module is configured to selectively open one or more of the valves to decrease the second pressure in the second portion after the increase in the second portion; and the diagnosis module configured to: selectively record the second pressure in the second portion based on a second derivative of the second pressure; and selectively diagnose a fault in the second accumulator based on the recorded second pressure.

In a feature, an accumulator checking system for a suspension system of a vehicle includes: a state module configured to selectively set a present state of an accumulator check for the suspension system to a first state; a valve module configured to determine first target open and closed states for valves of the suspension system based on the present state being set to the first state and to open and close the valves of the suspension system according to the first target open and closed states, respectively; a pump control module configured to, when the valves are in the first target open and closed states, respectively, selectively operate an electric pump of the suspension system in a first direction and increase a pressure of hydraulic fluid in a first portion of the suspension system including an accumulator; and a diagnosis module configured to: determine a total volume of hydraulic fluid input to the first portion of the suspension system while the pump control module operated the electric pump in the first direction and increased the pressure from a first predetermined pressure to a second predetermined pressure; and selectively diagnose the fault in the accumulator based on the total volume of hydraulic fluid input to the first portion.

In a feature, an accumulator checking method for a suspension system of a vehicle includes: selectively setting a present state of an accumulator check for the suspension system to a first state; determining first target open and closed states for valves of the suspension system based on the present state being set to the first state; selectively opening and closing the valves of the suspension system according to the first target open and closed states, respectively; when the valves are in the first target open and closed states, respectively, selectively operating an electric pump of the suspension system in a first direction and increasing a pressure of hydraulic fluid in a first portion of the suspension system including an accumulator; selectively opening one or more of the valves and decreasing the pressure in the first portion after the increasing; selectively recording the pressure in the first portion based on a second derivative of the pressure while the pressure is decreasing; and selectively diagnosing a fault in the accumulator based on the recorded pressure.

In further features, selectively recording includes recording the pressure in the first portion when the second derivative of the pressure is greater than a predetermined value.

In further features, the method further includes determining the second derivative of the pressure in the first portion.

In further features, determining the second derivative includes determining the second derivative of the pressure using a Savitzky Golay filter.

In further features, selectively diagnosing a fault includes diagnosing the fault in the accumulator when the recorded pressure is less than a predetermined pressure.

In further features, selectively diagnosing a fault includes diagnosing that no fault is present in the accumulator when the recorded pressure is greater than the predetermined pressure.

In further features, the method further includes: determining a total volume of hydraulic fluid input to the first portion of the suspension system while the pump control module operated the electric pump in the first direction and increased the pressure from a first predetermined pressure to a second predetermined pressure, where selectively diagnosing a fault includes diagnosing the fault in the accumulator further based on the total volume of hydraulic fluid input.

In further features, selectively diagnosing a fault includes diagnosing the fault when the total volume of hydraulic fluid input to the first portion is less than a predetermined volume.

In further features, selectively diagnosing a fault includes diagnosing that no fault is present in the accumulator when the total volume of hydraulic fluid input to the first portion is greater than the predetermined volume.

Further areas of applicability of the present disclosure will become apparent from the detailed description, the claims and the drawings. The detailed description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

The present disclosure will become more fully understood from the detailed description and the accompanying drawings, wherein:

FIG. 1 is a schematic diagram illustrating an example suspension system that includes two comfort valves that open and close the hydraulic lines connecting the two front dampers to the two rear dampers of the system;

FIG. 2 is a schematic diagram illustrating an example suspension system that includes two comfort valves that open and close the hydraulic lines connecting the two front dampers to the two rear dampers of the system and a separate hydraulic lifting circuit for the two front dampers;

FIG. 3 is a schematic diagram illustrating an example suspension system that includes two comfort valves that open and close the hydraulic lines connecting the two front dampers to the two rear dampers of the system and two separate hydraulic lifting circuits for the two front dampers and the two rear dampers;

FIG. 4 is a schematic diagram illustrating an example suspension system that includes four hydraulic circuits connecting the front and rear dampers and an example comfort valve equipped manifold assembly;

FIG. 5 is a schematic diagram illustrating the example comfort valve equipped manifold assembly illustrated in FIG. 4 ;

FIG. 6 is a schematic diagram illustrating an example suspension system that includes four hydraulic circuits connecting the front and rear dampers and an example comfort valve equipped manifold assembly;

FIG. 7 is a schematic diagram illustrating an example suspension system that includes four hydraulic circuits connecting the front and rear dampers and an example comfort valve equipped manifold assembly;

FIG. 8 includes a functional block diagram of an example implementation of a suspension control module;

FIG. 9 is a functional block diagram of an example implementation of an accumulator check module;

FIGS. 10A and 10B are a flowchart depicting an example method of checking accumulators of a suspension system; and

FIG. 11 includes a top graph of example pressure over time and a bottom graph of example second derivative of pressure over time.

In the drawings, reference numbers may be reused to identify similar and/or identical elements.

DETAILED DESCRIPTION

With reference to FIG. 1 , a suspension system 100 including a front left damper 102 a, a front right damper 102 b, a back left damper 102 c, and a back right damper 102 d. While it should be appreciated that the suspension system 100 described herein may include a different number of dampers than those shown in the drawings, in most automotive applications, four dampers are used at each corner of a vehicle to control vertical movements of the front and rear wheels of the vehicle. Thus, the front left damper 102 a controls (e.g., dampens) up and down (i.e., vertical) movements of the front left wheel of the vehicle, the front right damper 102 b controls (e.g., dampens) up and down (i.e., vertical) movements of the front right wheel of the vehicle, the back left damper 102 c controls (e.g., dampens) up and down (i.e., vertical) movements of the back left wheel of the vehicle, and the back right damper 102 d controls (e.g., dampens) up and down (i.e., vertical) movements of the back right wheel of the vehicle.

The suspension system 100 also includes a manifold assembly 104 that is connected in fluid communication with a pump assembly 106 by a pump hydraulic line 108. Although other configurations are possible, in the illustrated example, the pump assembly 106 includes a bi-directional pump 110, a hydraulic reservoir 112 (e.g., a tank), and a bypass hydraulic line 114 that can be open and closed by a pressure relief valve 116. The bi-directional pump 110 includes a first inlet/outlet port that is connected to the pump hydraulic line 108 and a second inlet/outlet port that is connected in fluid communication with the hydraulic reservoir 112 by a reservoir hydraulic line 118. The bi-directional pump 110 may operate (i.e., pump fluid) in two opposite directions depending on the polarity of the electricity that is supplied to the pump 110, so the first inlet/outlet port may operate as either an inlet port or an outlet port depending on the direction the bi-directional pump 110 is operating in and the same is true for the second inlet/outlet port of the bi-directional pump 110. In the example where the first inlet/outlet port is operating as an inlet port for the bi-directional pump 110 and the second inlet/outlet port is operating as an outlet port for the bi-directional pump 110, the bi-directional pump 110 draws in hydraulic fluid from the pump hydraulic line 108 via the first inlet/outlet port and discharges hydraulic fluid into the reservoir hydraulic line 118 via the second inlet/outlet port. As such, the bi-directional pump 110 produces a negative pressure in the pump hydraulic line 108 that can be used by manifold assembly 104 to reduced fluid pressure in the suspension system 100. In the example where the second inlet/outlet port is operating as an inlet port for the bi-directional pump 110 and the first inlet/outlet port is operating as an outlet port for the bi-directional pump 110, the bi-directional pump 110 draws in hydraulic fluid from the reservoir hydraulic line 118 via the second inlet/outlet port and discharges hydraulic fluid into the pump hydraulic line 108 via the first inlet/outlet port. As such, the bi-directional pump 110 produces a positive pressure in the pump hydraulic line 108 that can be used by manifold assembly 104 to increase fluid pressure in the suspension system 100. The bypass hydraulic line 114 runs from the pump hydraulic line 108 to the hydraulic reservoir 112 and bleeds fluid back into the hydraulic reservoir 112 when the pressure in the pump hydraulic line 108 exceeds a threshold pressure that causes the pressure relief valve 116 to open.

The manifold assembly 104 is connected in fluid communication with the front and rear dampers 102 a, 102 b, 102 c, 102 d by first and second hydraulic circuits 120 a, 120 b. The manifold assembly 104 includes first and second manifold valves 122 a, 122 b that are connected in parallel with the pump hydraulic line 108. The first hydraulic circuit 120 a is connected in fluid communication with the first manifold valve 122 a and the second hydraulic circuit 120 b is connected in fluid communication with the second manifold valve 122 b. The manifold assembly 104 also includes a first pressure sensor 124 a that is arranged to monitor the pressure in the first hydraulic circuit 120 a and a second pressure sensor 124 b that is arranged to monitor the pressure in the second hydraulic circuit 120 b. The bi-directional pump 110 of the pump assembly 106 and first and second pressure sensors 124 a, 124 b and the first and second manifold valves 122 a, 122 b of the manifold assembly 104 are electrically connected to a suspension control module 123, which is configured to activate (i.e., turn on in forward or reverse) the bi-directional pump 110 and electronically actuate (i.e., open and close) the first and second manifold valves 122 a, 122 b in response to various inputs, including signals from the first and second pressure sensors 124 a, 124 b. When the suspension control module 123 opens the first and second manifold valves 122 a, 122 b, the fluid pressure in the first and second hydraulic circuits 120 a, 120 b increases or decreases, respectively, depending on which direction the bi-directional pump 110 is running in.

The anti-roll capabilities of the suspension system 100 will be explained in greater detail below. However, from FIG. 1 it should be appreciated that fluid pressure in the first and second hydraulic circuits 120 a, 120 b operate to dynamically adjust the roll stiffness of the vehicle and can be used to either augment or completely replace mechanical stabilizer bars/anti-roll bars. Such mechanical systems require relatively straight, unobstructed runs between each of the front dampers 102 a, 102 b and each of the back dampers 102 c, 102 d. Accordingly, the suspension system 100 disclosed herein offers packaging benefits because the dampers 102 a, 102 b, 102 c, 102 d only need to be hydraulically connected to the manifold assembly 104 and to the suspension control module 123.

Each of the dampers 102 a, 102 b, 102 c, 102 d of the suspension system 100 includes a damper housing, a piston rod, and a piston that is mounted on the piston rod. The piston is arranged in sliding engagement with the inside of the damper housing such that the piston divides the damper housing into compression and rebound chambers. As such, the front left damper 102 a includes a first compression chamber 126 a and a first rebound chamber 128 a, the front right damper 102 b includes a second compression chamber 126 b and a second rebound chamber 128 b, the back left damper 102 c includes a third compression chamber 126 c and a third rebound chamber 128 c, and the back right damper 102 d includes a fourth compression chamber 126 d and a fourth rebound chamber 128 d.

In each damper 102 a, 102 b, 102 c, 102 d, the piston is a closed piston with no fluid flow paths defined within or by its structure. In addition, there are no other fluid flow paths in the damper housing such that no fluid is communicated between the compression and rebound chambers of the dampers 102 a, 102 b, 102 c, 102 d except through the first and second hydraulic circuits 120 a, 120 b. The rebound chambers 128 a, 128 b, 128 c, 128 d of the dampers 102 a, 102 b, 102 c, 102 d decrease in volume during rebound/extension strokes and increase in volume during compression strokes of the dampers 102 a, 102 b, 102 c, 102 d. The compression chambers 126 a, 126 b, 126 c, 126 d of the dampers 102 a, 102 b, 102 c, 102 d decrease in volume during compression strokes of the dampers 102 a, 102 b, 102 c, 102 d and increase in volume during rebound/extension strokes of the dampers 102 a, 102 b, 102 c, 102 d.

Each damper 102 a, 102 b, 102 c, 102 d also includes rebound and compression chamber ports 130 a, 130 b in the damper housing that are each provided with dampening valves. The rebound chamber port 130 a is arranged in fluid communication with the rebound chamber 128 a, 128 b, 128 c, 128 d of the damper 102 a, 102 b, 102 c, 102 d and the second port 130 b is arranged in fluid communication with the compression chamber 126 a, 126 b, 126 c, 126 d of the damper 102 a, 102 b, 102 c, 102 d. The dampening valves in the rebound and compression chamber ports 130 a, 130 b can be passive/spring-biased valves (e.g., spring-disc stacks) or active valves (e.g., electromechanical valves) and control fluid flow into and out of the compression and rebound chambers of the dampers 102 a, 102 b, 102 c, 102 d to provide one or more rebound dampening rates and compression dampening rates for each of the dampers 102 a, 102 b, 102 c, 102 d.

The first hydraulic circuit 120 a includes a first longitudinal hydraulic line 132 a that extends between and fluidly connects the second port 130 b (to the first compression chamber 126 a) of the front left damper 102 a and the second port 130 b (to the third compression chamber 126 c) of the back left damper 102 c. The first hydraulic circuit 120 a includes a front hydraulic line 134 a that extends between and fluidly connects the first longitudinal hydraulic line 132 a and the rebound chamber port 130 a (to the second rebound chamber 128 b) of the front right damper 102 b. The first hydraulic circuit 120 a also includes a rear hydraulic line 136 a that extends between and fluidly connects the first longitudinal hydraulic line 132 a and the rebound chamber port 130 a (to the fourth rebound chamber 128 d) of the back right damper 102 d. The first hydraulic circuit 120 a further includes a first manifold hydraulic line 138 a that extends between and fluidly connects the first longitudinal hydraulic line 132 a and the first manifold valve 122 a. The second hydraulic circuit 120 b includes a second longitudinal hydraulic line 132 b that extends between and fluidly connects the compression chamber port 130 b (to the second compression chamber 126 b) of the front right damper 102 b and the compression chamber port 130 b (to the fourth compression chamber 126 d) of the back right damper 102 d. The second hydraulic circuit 120 b includes a front hydraulic line 134 b that extends between and fluidly connects the second longitudinal hydraulic line 132 b and the rebound chamber port 130 a (to the first rebound chamber 128 a) of the front left damper 102 a. The second hydraulic circuit 120 b also includes a rear hydraulic line 136 b that extends between and fluidly connects the second longitudinal hydraulic line 132 b and the rebound chamber port 130 a (to the third rebound chamber 128 c) of the back left damper 102 c. The second hydraulic circuit 120 b further includes a second manifold hydraulic line 138 b that extends between and fluidly connects the second longitudinal hydraulic line 132 b and the second manifold valve 122 b. It should be appreciated that the word “longitudinal” as used in the first and second longitudinal hydraulic lines 132 a, 132 b simply means that the first and second longitudinal hydraulic lines 132 a, 132 b run between the front dampers 102 a, 102 b and the back dampers 102 c, 102 d generally. The first and second longitudinal hydraulic lines 132 a, 132 b need not be linear or arranged in any particular direction as long as they ultimately connect the front dampers 102 a, 102 b and the back dampers 102 c, 102 d.

The suspension system 100 also includes four bridge hydraulic lines 140 a, 140 b, 140 c, 140 d that fluidly couple the first and second hydraulic circuits 120 a, 120 b and each corner of the vehicle. The four bridge hydraulic lines 140 a, 140 b, 140 c, 140 d include a front left bridge hydraulic line 140 a that extends between and fluidly connects the first longitudinal hydraulic line 132 a of the first hydraulic circuit 120 a and the front hydraulic line 134 b of the second hydraulic circuit 120 b, a front right bridge hydraulic line 140 b that extends between and fluidly connects the front hydraulic line 134 a of the first hydraulic circuit 120 a and the second longitudinal hydraulic line 132 b of the second hydraulic circuit 120 b, a back left bridge hydraulic line 140 c that extends between and fluidly connects the first longitudinal hydraulic line 132 a of the first hydraulic circuit 120 a and the rear hydraulic line 136 b of the second hydraulic circuit 120 b, and a back right bridge hydraulic line 140 d that extends between and fluidly connects the rear hydraulic line 136 a of the first hydraulic circuit 120 a and the second longitudinal hydraulic line 132 b of the second hydraulic circuit 120 b.

The front left bridge hydraulic line 140 a is connected to the first longitudinal hydraulic line 132 a between the compression chamber port 130 b of the front left damper 102 a and the front hydraulic line 134 a of the first hydraulic circuit 120 a. The front right bridge hydraulic line 140 b is connected to the second longitudinal hydraulic line 132 b between the compression chamber port 130 b of the front right damper 102 b and the front hydraulic line 134 b of the second hydraulic circuit 120 b. The back left bridge hydraulic line 140 c is connected to the first longitudinal hydraulic line 132 a between the compression chamber port 130 b of the back left damper 102 c and the rear hydraulic line 136 a of the first hydraulic circuit 120 a. The back right bridge hydraulic line 140 d is connected to the second longitudinal hydraulic line 132 b between the compression chamber port 130 b of the back right damper 102 d and the rear hydraulic line 136 b of the second hydraulic circuit 120 b. In the illustrated example, the various hydraulic lines are made of flexible tubing (e.g., hydraulic hoses), but it should be appreciated that other conduit structures and/or fluid passageways can be used.

A front left accumulator 142 a is arranged in fluid communication with the first longitudinal hydraulic line 132 a at a location between the compression chamber port 130 b of the front left damper 102 a and the front left bridge hydraulic line 140 a. A front right accumulator 142 b is arranged in fluid communication with the second longitudinal hydraulic line 132 b at a location between the compression chamber port 130 b of the front right damper 102 b and the front right bridge hydraulic line 140 b. A back left accumulator 142 c is arranged in fluid communication with the first longitudinal hydraulic line 132 a at a location between the compression chamber port 130 b of the back left damper 102 c and the back left bridge hydraulic line 140 c. A back right accumulator 142 d is arranged in fluid communication with the second longitudinal hydraulic line 132 b at a location between the compression chamber port 130 b of the back right damper 102 d and the back right bridge hydraulic line 140 d. Each of the accumulators 142 a, 142 b, 142 c, 142 d have a variable fluid volume that increases and decreases depending on the fluid pressure in the first and second longitudinal hydraulic lines 132 a, 132 b. It should be appreciated that the accumulators 142 a, 142 b, 142 c, 142 d may be constructed in a number of different ways. For example and without limitation, the accumulators 142 a, 142 b, 142 c, 142 d may have accumulation chambers and pressurized gas chambers that are separated by floating pistons or flexible membranes.

The suspension system 100 also includes six electro-mechanical comfort valves 144 a, 144 b, 144 c, 144 d, 146 a, 146 b that are connected in-line (i.e., in series) with each of the bridge hydraulic lines 140 a, 140 b, 140 c, 140 d and each of the longitudinal hydraulic lines 132 a, 132 b. A front left comfort valve 144 a is positioned in the front left bridge hydraulic line 140 a. A front right comfort valve 144 b is positioned in the front right bridge hydraulic line 140 b. A back left comfort valve 144 c is positioned in the back left bridge hydraulic line 140 c. A back right comfort valve 144 d is positioned in the back right bridge hydraulic line 140 d. A first longitudinal comfort valve 146 a is positioned in the first longitudinal hydraulic line 132 a between the front and rear hydraulic lines 134 a, 136 a of the first hydraulic circuit 120 a. A second longitudinal comfort valve 146 b is positioned in the second longitudinal hydraulic line 132 b between the front and rear hydraulic lines 134 b, 136 b of the second hydraulic circuit 120 b. In the illustrated example, the comfort valves 144 a, 144 b, 144 c, 144 d and the longitudinal comfort valves 146 a, 146 b are semi-active electro-mechanical valves with a combination of passive spring-disk elements and a solenoid. The comfort valves 144 a, 144 b, 144 c, 144 d and the longitudinal comfort valves 146 a, 146 b are electronically connected to the suspension control module 123, which is configured to supply electrical current to the solenoids of the comfort valves 144 a, 144 b, 144 c, 144 d and the longitudinal comfort valves 146 a, 146 b to selectively and individually open and close the comfort valves 144 a, 144 b, 144 c, 144 d and the longitudinal comfort valves 146 a, 146 b.

The first pressure sensor 124 a of the manifold assembly 104 is arranged to measure fluid pressure in the first manifold hydraulic line 138 a and the second pressure sensor 124 b of the manifold assembly 104 is arranged to measure fluid pressure in the second manifold hydraulic line 138 b. When the vehicle is cornering, braking, or accelerating, the lateral and longitudinal acceleration is measured by one or more accelerometers (not shown) and the anti-roll torque to control the roll of the vehicle is calculated by the suspension control module 123. Alternatively, the lateral and longitudinal acceleration of the vehicle can be computed by the suspension control module 123 based on a variety of different inputs, including without limitation, steering angle, vehicle speed, brake pedal position, and/or accelerator pedal position. The dampers 102 a, 102 b, 102 c, 102 d are used to provide forces that counteract the roll moment induced by the lateral acceleration, thus reducing the roll angle of the vehicle.

When the first and second manifold valves 122 a, 122 b are closed, the first and second hydraulic circuits 120 a, 120 b operate as a closed loop system, either together or separately depending on the open or closed status of the electro-mechanical comfort valves 144 a, 144 b, 144 c, 144 d and the longitudinal comfort valves 146 a, 146 b. When the first and/or second manifold valves 122 a, 122 b are open, the bi-directional pump 110 either adds or removes fluid from the first and/or second hydraulic circuits 120 a, 120 b. As will be explained in greater detail below, the suspension system 100 can control the roll stiffness of the vehicle, which changes the degree to which the vehicle will lean to one side or the other during corning (i.e., roll)

For example, when the vehicle is put into a right-hand turn, the momentum of the sprung weight of the vehicle tends to make the vehicle lean left towards the outside of the turn, compressing the front left damper 102 a and the back left damper 102 c. When this occurs, fluid flows out from the first compression chamber 126 a of the front left damper 102 a and the third compression chamber 126 c of the back left damper 102 c into the first longitudinal hydraulic line 132 a of the first hydraulic circuit 120 a. As a result of the weight transfer to the left side of the vehicle, the front right damper 102 b and back right damper 102 d begin to extend, causing fluid to flow out of the second rebound chamber 128 b of the front right damper 102 b and the fourth rebound chamber 128 d of the back right damper 102 d into the front and rear hydraulic lines 134 a, 136 a of the first hydraulic circuit 120 a. When the comfort valves 144 a, 144 b, 144 c, 144 d are closed, the fluid flow out of the first compression chamber 126 a of the front left damper 102 a, out of the third compression chamber 126 c of the back left damper 102 c, out of the second rebound chamber 128 b of the front right damper 102 b, and out of the fourth rebound chamber 128 d of the back right damper 102 d and into the front and rear hydraulic lines 134 a, 136 a of the first hydraulic circuit 120 a increases the pressure in the front left and back left accumulators 142 a, 142 c, thus providing a passive roll resistance where it becomes increasingly more difficult to compress the front left damper 102 a and the back left damper 102 c since the first compression chamber 126 a of the front left damper 102 a and the third compression chamber 126 c of the back left damper 102 c are connected in fluid communication with the first hydraulic circuit 120 a. At the same time, fluid flows out of front left and back left accumulators 142 b, 142 d and into the first rebound chamber 128 a of the front left damper 102 a, into the third rebound chamber 128 c of the back left damper 102 c, into the second compression chamber 126 b of the front right damper 102 b, and into the fourth compression chamber 126 d of the back right damper 102 d. The resulting pressure difference between the dampers 102 a, 102 b, 102 c, 102 d generates damper forces that counteract or resist the roll moment of the vehicle. Additional roll resistance can be added by opening the first manifold valve 122 a as the bi-directional pump 110 is running in a first direction where the bi-directional pump 110 draws in hydraulic fluid from the reservoir hydraulic line 118 and discharges hydraulic fluid into the pump hydraulic line 108 to produce a positive pressure in the pump hydraulic line 108, which increases fluid pressure in the first hydraulic circuit 120 a when the first manifold valve 122 a is open.

The opposite is true when the vehicle is put into a left-hand turn, where the momentum of the sprung weight of the vehicle tends to make the vehicle lean right towards the outside of the turn, compressing the front right damper 102 b and the back right damper 102 d. When this occurs, fluid flows out from the second compression chamber 126 b of the front right damper 102 b and the fourth compression chamber 126 d of the back right damper 102 d into the second longitudinal hydraulic line 132 b of the second hydraulic circuit 120 b. As a result of the weight transfer to the right side of the vehicle, the front left damper 102 a and back left damper 102 c begin to extend, causing fluid to flow out of the first rebound chamber 128 a of the front left damper 102 a and the third rebound chamber 128 c of the back left damper 102 c into the front and rear hydraulic lines 134 b, 136 b of the second hydraulic circuit 120 b. When the comfort valves 144 a, 144 b, 144 c, 144 d are closed, the fluid flow out of the second compression chamber 126 b of the front right damper 102 b, out of the fourth compression chamber 126 d of the back right damper 102 d, out of the first rebound chamber 128 a of the front left damper 102 a, and out of the third rebound chamber 128 c of the back left damper 102 c and into the front and rear hydraulic lines 134 b, 136 b of the second hydraulic circuit 120 b increases the pressure in the front right and back right accumulators 142 b, 142 d, thus providing a passive roll resistance where it becomes increasingly more difficult to compress the front right damper 102 b and the back right damper 102 d since the second compression chamber 126 b of the front right damper 102 b and the fourth compression chamber 126 d of the back right damper 102 d are connected in fluid communication with the second hydraulic circuit 120 b. At the same time, fluid flows out of front right and back right accumulators 142 a, 142 c and into the second rebound chamber 128 b of the front right damper 102 b, into the fourth rebound chamber 128 d of the back right damper 102 d, into the first compression chamber 126 a of the front left damper 102 a, and into the third compression chamber 126 c of the back left damper 102 c. The resulting pressure difference between the dampers 102 a, 102 b, 102 c, 102 d generates damper forces that counteract or resist the roll moment of the vehicle. Additional roll resistance can be added by opening the second manifold valve 122 b as the bi-directional pump 110 is running in the first direction where the bi-directional pump 110 draws in hydraulic fluid from the reservoir hydraulic line 118 and discharges hydraulic fluid into the pump hydraulic line 108 to produce a positive pressure in the pump hydraulic line 108, which increases fluid pressure in the second hydraulic circuit 120 b when the second manifold valve 122 b is open.

When roll stiffness is not required, the comfort valves 144 a, 144 b, 144 c, 144 d and the longitudinal comfort valves 146 a, 146 b can be opened to enhance the ride comfort of the suspension system 100 and reduce or eliminate unwanted suspension movements resulting from the hydraulic coupling of one damper of the system to another damper of the system (e.g., where the compression of one damper causes movement and/or a dampening change in another damper). For example, when the front left comfort valve 144 a is open and the front left damper 102 a undergoes a compression stroke as the front left wheel hits a bump, fluid may flow from the first compression chamber 126 a of the front left damper 102 a, into the first longitudinal hydraulic line 132 a, from the first longitudinal hydraulic line 132 a to the front hydraulic line 134 b of the second hydraulic circuit 120 b by passing through the front left bridge hydraulic line 140 a and the front left comfort valve 144 a, and into the first rebound chamber 128 a of the front left damper 102 a. Thus, fluid can travel from the first compression chamber 126 a to the first rebound chamber 128 a of the front left damper 102 a with the only restriction coming from the dampening valves in the rebound and compression chamber ports 130 a, 130 b of the front left damper 102 a. As such, when all of the comfort valves 144 a, 144 b, 144 c, 144 d and the longitudinal comfort valves 146 a, 146 b are open, the dampers 102 a, 102 b, 102 c, 102 d are effectively decoupled from one another for improved ride comfort. It should also be appreciated that to return the suspension system 100 to this “comfort mode” of operation, the first and/or second manifold valves 122 a, 122 b may be opened while the bi-directional pump 110 is running in a second direction where the bi-directional pump 110 draws in hydraulic fluid from the pump hydraulic line 108 and discharges hydraulic fluid into the reservoir hydraulic line 118 to produce a negative pressure in the pump hydraulic line 108 that reduces fluid pressure in the first and/or second hydraulic circuits 120 a, 120 b.

FIG. 2 illustrates another suspension system 200 that shares many of the same components as the suspension system 100 illustrated in FIG. 1 , but in FIG. 2 a front axle lift assembly 248 has been added. Rather than repeat the description set forth above, the following paragraphs describe the structure and function of the components in FIG. 2 that are new and/or different from those shown and described in connection with FIG. 1 . It should be appreciated that the reference numbers in FIG. 1 are “100” series numbers (e.g., 100, 102, 104, etc.) whereas the components in FIG. 2 that are the same or similar to the components of the suspension system 100 shown in FIG. 1 share the same base reference numbers, but are listed as “200” series numbers (e.g., 200, 202, 204, etc.). Thus, the same description for element 100 above applies to element 200 in FIG. 2 and so on and so forth.

The front axle lift assembly 248 illustrated in FIG. 2 includes a front left lifter 250 a on the front left damper 202 a and a front right lifter 250 b on the front right damper 202 b. Although other configurations are possible, in the illustrated example, the front left damper 202 a and the front right damper 202 b include a front left coil spring 252 a and a front right coil spring 252 b, respectively, that extend co-axially and helically about the piston rods of the front dampers 202 a, 202 b in a coil-over arrangement. The front lifters 250 a, 250 b are positioned between the front coils springs 252 a, 252 b and the first and second rebound chambers 228 a, 228 b of the front dampers 202 a, 202 b and extend co-axially and annularly about the piston rods. The manifold assembly 204 further includes a third manifold valve 222 c that is connected in fluid communication with the pump hydraulic line 208. A front axle lift hydraulic line 254 a extends between and is fluidly connected to the third manifold valve 222 c with the front left lifter 250 a and the front right lifter 250 b. A third pressure sensor 224 c is arranged to monitor the fluid pressure in the front axle lift hydraulic line 254 a. Each front lifter 250 a, 250 b is axially expandable such that an increase in fluid pressure inside the front lifters 250 a, 250 b causes the front lifters 250 a, 250 b to urge the front coil springs 252 a, 252 b away from the first and second rebound chambers 228 a, 228 b of the front dampers 202 a, 202 b, which operates to lift (i.e., raise) the front of the vehicle, increasing the ride height. To activate the front axle lift assembly 248, the suspension control module 123 opens the third manifold valve 222 c when the bi-directional pump 210 is running in the first direction where the bi-directional pump 210 draws in hydraulic fluid from the reservoir hydraulic line 218 and discharges hydraulic fluid into the pump hydraulic line 208 to produce a positive pressure in the pump hydraulic line 208, which increases fluid pressure in the front axle lift hydraulic line 254 a and thus the front lifters 250 a, 250 b. Once a desired lift position is achieved, the controller closes the third manifold valve 222 c. It should therefore be appreciated that the front axle lift assembly 248 can be used to provide improved ground clearance during off-road operation or to give low riding vehicles improved ground clearance when traversing speed bumps. To deactivate the front axle lift assembly 248, the suspension control module 123 opens the third manifold valve 222 c when the bi-directional pump 210 is running in the second direction where the bi-directional pump 210 draws in hydraulic fluid from the pump hydraulic line 208 and discharges hydraulic fluid into the reservoir hydraulic line 218 to produce a negative pressure in the pump hydraulic line 208 that reduces fluid pressure in the front axle lift hydraulic line 254 a to lower the front of the vehicle back down to an unlifted position.

FIG. 3 illustrates another suspension system 300 that shares many of the same components as the suspension systems 100, 200 illustrated in FIGS. 1 and 2 , but in FIG. 3 a rear axle lift assembly 356 has been added. Rather than repeat the description set forth above, the following paragraphs describe the structure and function of the components in FIG. 3 that are new and/or different from those shown and described in connection with FIGS. 1 and 2 . It should be appreciated that the reference numbers in FIG. 1 are “100” series numbers (e.g., 100, 102, 104, etc.) and the reference numbers in FIG. 2 are “200” series numbers (e.g., 200, 202, 204, etc.) whereas the components in FIG. 3 that are the same or similar to the components of the suspension systems 100, 200 shown in FIGS. 1 and 2 share the same base reference numbers, but are listed as “300” series numbers (e.g., 300, 302, 304, etc.). Thus, the same description for elements 100 and 200 above applies to element 300 in FIG. 3 and so on and so forth.

The rear axle lift assembly 356 illustrated in FIG. 3 includes a back left lifter 350 c on the back left damper 302 c and a back right lifter 350 d on the back right damper 302 d. Although other configurations are possible, in the illustrated example, the back left damper 302 c and the back right damper 302 d include a back left coil spring 352 c and a back right coil spring 352 d, respectively, that extend co-axially and helically about the piston rods of the back dampers 302 c, 302 d in a coil-over arrangement. The back lifters 350 c, 350 d are positioned between the back coils springs 352 c, 352 d and the third and fourth rebound chambers 328 c, 328 d of the back dampers 302 a, 302 b and extend co-axially and annularly about the piston rods. The manifold assembly 304 further includes a fourth manifold valve 322 d that is connected in fluid communication with the pump hydraulic line 308. A rear axle lift hydraulic line 354 b extends between and is fluidly connected to the fourth manifold valve 322 d with the back left lifter 350 c and the back right lifter 350 d. A fourth pressure sensor 324 d is arranged to monitor the fluid pressure in the rear axle lift hydraulic line 354 b. Each back lifter 350 c, 350 d is axially expandable such that an increase in fluid pressure inside the back lifters 350 c, 350 d causes the back lifters 350 c, 350 d to urge the back coil springs 352 c, 352 d away from the third and fourth rebound chambers 328 c, 328 d of the back dampers 302 c, 302 d, which operates to lift (i.e., raise) the back/rear of the vehicle, increasing the ride height. To activate the rear axle lift assembly 356, the suspension control module 123 opens the fourth manifold valve 322 d when the bi-directional pump 310 is running in the first direction where the bi-directional pump 310 draws in hydraulic fluid from the reservoir hydraulic line 318 and discharges hydraulic fluid into the pump hydraulic line 308 to produce a positive pressure in the pump hydraulic line 308, which increases fluid pressure in the rear axle lift hydraulic line 354 b and thus the back lifters 350 c, 350 d. Once a desired lift position is achieved, the suspension control module 123 closes the fourth manifold valve 322 d. It should therefore be appreciated that the rear axle lift assembly 356 can be used in combination with the front axle lift assembly 348 (also described above in connection with FIG. 2 ) to provide improved ground clearance during off-road operation or to give low riding vehicles improved ground clearance when traversing speed bumps. To deactivate the rear axle lift assembly 356, the suspension control module 123 opens the fourth manifold valve 322 d when the bi-directional pump 310 is running in the second direction where the bi-directional pump 310 draws in hydraulic fluid from the pump hydraulic line 308 and discharges hydraulic fluid into the reservoir hydraulic line 318 to produce a negative pressure in the pump hydraulic line 308 that reduces fluid pressure in the rear axle lift hydraulic line 354 b to lower the rear of the vehicle back down to an unlifted position.

With reference to FIG. 4 , another suspension system 400 is illustrated that shares many of the same components as the suspension system 100 illustrated in FIG. 1 . Rather than repeat the description set forth above, the following paragraphs describe the structure and function of the components in FIG. 4 that are new and/or different from those shown and described in connection with FIG. 1 . It should be appreciated that the reference numbers in FIG. 1 are “100” series numbers (e.g., 100, 102, 104, etc.) whereas the components in FIG. 4 that are the same or similar to the components of the suspension system 100 shown in FIG. 1 share the same base reference numbers, but are listed as “400” series numbers (e.g., 400, 402, 404, etc.). Thus, the same description for element 100 above applies to element 400 in FIG. 4 and so on and so forth.

The suspension system 400 in FIG. 4 also includes a front left damper 402 a, a front right damper 402 b, a back left damper 402 c, and a back right damper 402 d. The suspension system 400 also includes a manifold assembly 404 that is connected in fluid communication with a pump assembly 406 by a pump hydraulic line 408. Like in FIG. 1 , the pump assembly 406 includes a bi-directional pump 410, a hydraulic reservoir 412 (e.g., a tank), and a bypass hydraulic line 414 that can be open and closed by a pressure relief valve 416.

The manifold assembly 404 is connected in fluid communication with the front and rear dampers 402 a, 402 b, 402 c, 402 d by four hydraulic circuits 420 a, 420 b, 420 c, 420 d: a first hydraulic circuit 420 a, a second hydraulic circuit 420 b, a third hydraulic circuit 420 c, and a fourth hydraulic circuit 420 d. The manifold assembly 404 includes four manifold valves 422 a, 422 b, 422 c, 422 d (a first manifold valve 422 a, a second manifold valve 422 b, a third manifold valve 422 c, and a fourth manifold valve 422 d) that are connected in parallel with the pump hydraulic line 408. The manifold assembly 404 further includes a first manifold comfort valve 460 a, a second manifold comfort valve 460 b, and six manifold conduits 462 a, 462 b, 462 c, 462 d, 462 e, 462 f: a first manifold conduit 462 a, a second manifold conduit 462 b, a third manifold conduit 462 c, a fourth manifold conduit 462 d, a fifth manifold conduit 462 e, and a sixth manifold conduit 462 f. The first manifold conduit 462 a is connected in fluid communication with the first manifold valve 422 a and the first manifold comfort valve 460 a while the second manifold conduit 462 b is connected in fluid communication with the second manifold valve 422 b and the second manifold comfort valve 460 b. The third manifold conduit 462 c is connected in fluid communication with the third manifold valve 422 c and the fourth manifold conduit 462 d is connected in fluid communication with the fourth manifold valve 422 d. The fifth manifold conduit 462 e is connected in fluid communication with the first manifold comfort valve 460 a and the sixth manifold conduit 462 f is connected in fluid communication with the second manifold comfort valve 460 b. Additional structure and operational details of the manifold assembly 404 is described below in connection with FIG. 5 ; however, it should be appreciated from FIG. 4 that fluid pressure in the four hydraulic circuits 420 a, 420 b, 420 c, 420 d operates to dynamically adjust the roll and pitch stiffness of the vehicle and can be used to either augment or completely replace mechanical stabilizer bars/anti-roll bars. Such mechanical systems require relatively straight, unobstructed runs between each of the front dampers 402 a, 402 b and each of the back dampers 402 c, 402 d. Accordingly, the suspension system 400 disclosed herein offers packaging benefits because the dampers 402 a, 402 b, 402 c, 402 d only need to be hydraulically connected to the manifold assembly 404.

The first hydraulic circuit 420 a includes a first cross-over hydraulic line 464 a that extends between and fluidly connects the compression chamber port 430 b (to the first compression chamber 426 a) of the front left damper 402 a and the rebound chamber port 430 a (to the fourth rebound chamber 428 d) of the back right damper 402 d. The first hydraulic circuit 420 a also includes a first manifold hydraulic line 438 a that extends between and fluidly connects the first cross-over hydraulic line 464 a and the first manifold conduit 462 a. The second hydraulic circuit 420 b includes a second cross-over hydraulic line 464 b that extends between and fluidly connects the compression chamber port 430 b (to the second compression chamber 426 b) of the front right damper 402 b and the rebound chamber port 430 a (to the third rebound chamber 428 c) of the back left damper 402 c. The second hydraulic circuit 420 b also includes a second manifold hydraulic line 438 b that extends between and fluidly connects the second cross-over hydraulic line 464 b and the second manifold conduit 462 b. The third hydraulic circuit 420 c includes a third cross-over hydraulic line 464 c that extends between and fluidly connects the rebound chamber port 430 a (to the first rebound chamber 428 a) of the front left damper 402 a and the compression chamber port 430 b (to the fourth compression chamber 426 d) of the back right damper 402 d. The third hydraulic circuit 420 c also includes a third manifold hydraulic line 438 c that extends between and fluidly connects the third cross-over hydraulic line 464 c and the sixth manifold conduit 462 f. The fourth hydraulic circuit 420 d includes a fourth cross-over hydraulic line 464 d that extends between and fluidly connects the rebound chamber port 430 a (to the second rebound chamber 428 b) of the front right damper 402 b and the compression chamber port 430 b (to the third compression chamber 426 c) of the back left damper 402 c. The fourth hydraulic circuit 420 d also includes a fourth manifold hydraulic line 438 d that extends between and fluidly connects the fourth cross-over hydraulic line 464 d and the fifth manifold conduit 462 e. It should be appreciated that the word “cross-over” as used in the first, second, third, and fourth cross-over hydraulic lines 464 a, 464 b, 464 c, 464 d simply means that the first, second, third, and fourth cross-over hydraulic lines 464 a, 464 b, 464 c, 464 d run between dampers 402 a, 402 b, 402 c, 402 d at opposite corners of the vehicle (e.g., front left to back right and front right to back left). The first, second, third, and fourth cross-over hydraulic lines 464 a, 464 b, 464 c, 464 d need not be linear or arranged in any particular direction as long as they ultimately connect dampers 402 a, 402 b, 402 c, 402 d positioned at opposite corners of the vehicle.

The suspension system 400 also includes four bridge hydraulic lines 440 a, 440 b, 440 c, 440 d that fluidly couple the first and third hydraulic circuits 420 a, 420 c and the second and fourth hydraulic circuits 420 b, 420 d to one another. The four bridge hydraulic lines 440 a, 440 b, 440 c, 440 d include a front left bridge hydraulic line 440 a that extends between and fluidly connects the first cross-over hydraulic line 464 a and the third cross-over hydraulic line 464 c, a front right bridge hydraulic line 440 b that extends between and fluidly connects the second cross-over hydraulic line 464 b and the fourth cross-over hydraulic line 464 d, a back left bridge hydraulic line 440 c that extends between and fluidly connects the second cross-over hydraulic line 464 b and the fourth cross-over hydraulic line 464 d, and a back right bridge hydraulic line 440 d that extends between and fluidly connects the first cross-over hydraulic line 464 a and the third cross-over hydraulic line 464 c.

The front left bridge hydraulic line 440 a is connected to the first cross-over hydraulic line 464 a between the compression chamber port 430 b of the front left damper 402 a and the first manifold hydraulic line 438 a and is connected to the third cross-over hydraulic line 464 c between the rebound chamber port 430 a of the front left damper 402 a and the third manifold hydraulic line 438 c. The front right bridge hydraulic line 440 b is connected to the second cross-over hydraulic line 464 b between the compression chamber port 430 b of the front right damper 402 b and the second manifold hydraulic line 438 b and is connected to the fourth cross-over hydraulic line 464 d between the rebound chamber port 430 a of the front right damper 402 b and the fourth manifold hydraulic line 438 d. The back left bridge hydraulic line 440 c is connected to the second cross-over hydraulic line 464 b between the rebound chamber port 430 a of the back left damper 402 c and the second manifold hydraulic line 438 b and is connected to the fourth cross-over hydraulic line 464 d between the compression chamber port 430 b of the back left damper 402 c and the fourth manifold hydraulic line 438 d. The back right bridge hydraulic line 440 d is connected to the first cross-over hydraulic line 464 a between the rebound chamber port 430 a of the back right damper 402 d and the first manifold hydraulic line 438 a and is connected to the third cross-over hydraulic line 464 c between the compression chamber port 430 b of the back right damper 402 d and the third manifold hydraulic line 438 c. In the illustrated example, the various hydraulic lines are made of flexible tubing (e.g., hydraulic hoses), but it should be appreciated that other conduit structures and/or fluid passageways can be used.

A front left accumulator 442 a is arranged in fluid communication with the first cross-over hydraulic line 464 a at a location between the compression chamber port 430 b of the front left damper 402 a and the front left bridge hydraulic line 440 a. A front right accumulator 442 b is arranged in fluid communication with the second cross-over hydraulic line 464 b at a location between the compression chamber port 430 b of the front right damper 402 b and the front right bridge hydraulic line 440 b. A back left accumulator 442 c is arranged in fluid communication with the fourth cross-over hydraulic line 464 d at a location between the compression chamber port 430 b of the back left damper 402 c and the back left bridge hydraulic circuit 420 c. A back right accumulator 442 d is arranged in fluid communication with the third cross-over hydraulic line 464 c at a location between the compression chamber port 430 b of the back right damper 402 d and the back right bridge hydraulic line 440 d. Each of the accumulators 442 a, 442 b, 442 c, 442 d have a variable fluid volume that increases and decreases depending on the fluid pressure in the first and second longitudinal hydraulic lines 432 a, 432 b. It should be appreciated that the accumulators 442 a, 442 b, 442 c, 442 d may be constructed in a number of different ways. For example and without limitation, the accumulators 442 a, 442 b, 442 c, 442 d may have accumulation chambers and pressurized gas chambers that are separated by floating pistons or flexible membranes.

The suspension system 400 also includes four electro-mechanical comfort valves 444 a, 444 b, 444 c, 444 d that are connected in-line (i.e., in series) with each of the bridge hydraulic lines 440 a, 440 b, 440 c, 440 d. A front left comfort valve 444 a is positioned in the front left bridge hydraulic line 440 a. A front right comfort valve 444 b is positioned in the front right bridge hydraulic line 440 b. A back left comfort valve 444 c is positioned in the back left bridge hydraulic line 440 c. A back right comfort valve 444 d is positioned in the back right bridge hydraulic line 440 d. In the illustrated example, the four comfort valves 444 a, 444 b, 444 c, 444 d and the two manifold comfort valves 460 a, 460 b are semi-active electro-mechanical valves with a combination of passive spring-disk elements and a solenoid. The comfort valves 444 a, 444 b, 444 c, 444 d and the two manifold comfort valves 460 a, 460 b are electronically connected to the suspension control module 123, which is configured to supply electrical current to the solenoids of the comfort valves 444 a, 444 b, 444 c, 444 d and the two manifold comfort valves 460 a, 460 b to selectively and individually open and close the comfort valves 444 a, 444 b, 444 c, 444 d and the two manifold comfort valves 460 a, 460 b.

When the manifold valves 422 a, 422 b, 422 c, 422 d are closed, the hydraulic circuits 420 a, 420 b, 420 c, 420 d operate as a closed loop system, either together or separately depending on the open or closed status of the comfort valves 444 a, 444 b, 444 c, 444 d and manifold comfort valves 460 a, 460 b. When the manifold valves 422 a, 422 b, 422 c, 422 d are open, the bi-directional pump 110 either adds or removes fluid from one or more of the hydraulic circuits 420 a, 420 b, 420 c, 420 d. There are three primary types of suspension movements that the illustrated suspension system 400 can control either passively (i.e., as a closed loop system) or actively (i.e., as an open loop system) by changing or adapting the roll and/or pitch stiffness of the vehicle: leaning to one side or the other during cornering (i.e., roll) pitching forward during braking (i.e., brake dive), and pitching aft during acceleration (i.e., rear end squat). Descriptions of how the suspension system 400 reacts to each of these conditions are provided below.

When the vehicle is put into a right-hand turn, the momentum of the sprung weight of the vehicle tends to make the vehicle lean left towards the outside of the turn, compressing the front left damper 402 a and the back left damper 402 c. When this occurs, fluid flows out from the first compression chamber 426 a of the front left damper 402 a and the third compression chamber 426 c of the back left damper 402 c into the first and fourth cross-over hydraulic lines 464 a, 464 d. As a result of the weight transfer to the left side of the vehicle, the front right damper 402 b and back right damper 402 d begin to extend, causing fluid to flow out of the second rebound chamber 428 b of the front right damper 402 b and the fourth rebound chamber 428 d of the back right damper 402 d into the first and fourth cross-over hydraulic lines 464 a, 464 d. When the comfort valves 444 a, 444 b, 444 c, 444 d are closed, the fluid flow out of the first compression chamber 426 a of the front left damper 402 a, out of the third compression chamber 426 c of the back left damper 402 c, out of the second rebound chamber 428 b of the front right damper 402 b and out of the fourth rebound chamber 428 d of the back right damper 402 d and into the first and fourth cross-over hydraulic lines 464 a, 464 d increases the pressure in the front left and back left accumulators 442 a, 442 c, thus providing a passive roll resistance where it becomes increasingly more difficult to compress the front left damper 402 a and the back left damper 402 c since the first compression chamber 426 a of the front left damper 402 a and the third compression chamber 426 c of the back left damper 402 c are connected in fluid communication with the first and fourth hydraulic circuits 420 a, 420 d. At the same time, fluid flows out of front left and back left accumulators 442 b, 442 d and into the first rebound chamber 428 a of the front left damper 402 a, into the third rebound chamber 428 c of the back left damper 402 c, into the second compression chamber 426 b of the front right damper 402 b, and into the fourth compression chamber 426 d of the back right damper 402 d. The resulting pressure difference between the dampers 402 a, 402 b, 402 c, 402 d generates damper forces that counteract or resist the roll moment of the vehicle. Additional roll resistance can be added by opening the first manifold valve 422 a and the first manifold comfort valve 460 a as the bi-directional pump 410 is running in a first direction where the bi-directional pump 410 draws in hydraulic fluid from the reservoir hydraulic line 418 and discharges hydraulic fluid into the pump hydraulic line 408 to produce a positive pressure in the pump hydraulic line 408, which increases fluid pressure in the first and fourth hydraulic circuits 420 a, 420 d.

The opposite is true when the vehicle is put into a left-hand turn, where the momentum of the sprung weight of the vehicle tends to make the vehicle lean right towards the outside of the turn, compressing the front right damper 402 b and the back right damper 402 d. When this occurs, fluid flows out from the second compression chamber 426 b of the front right damper 402 b and the fourth compression chamber 426 d of the back right damper 402 d into the second and third cross-over hydraulic lines 464 b, 464 c. As a result of the weight transfer to the right side of the vehicle, the front left damper 402 a and back left damper 402 c begin to extend, causing fluid to flow out of the first rebound chamber 428 a of the front left damper 402 a and the third rebound chamber 428 c of the back left damper 402 c into the second and third cross-over hydraulic lines 464 b, 464 c. When the comfort valves 444 a, 444 b, 444 c, 444 d are closed, the fluid flow out of the second compression chamber 426 b of the front right damper 402 b, out of the fourth compression chamber 426 d of the back right damper 402 d, out of the first rebound chamber 428 a of the front left damper 402 a, and out of the third rebound chamber 428 c of the back left damper 402 c and into the second and third cross-over hydraulic lines 464 b, 464 c increases the pressure in the front right and back right accumulators 142 b, 142 d, thus providing a passive roll resistance where it becomes increasingly more difficult to compress the front right damper 402 b and the back right damper 402 d since the second compression chamber 426 b of the front right damper 402 b and the fourth compression chamber 426 d of the back right damper 402 d are connected in fluid communication with the second and third hydraulic circuits 420 b, 420 c. At the same time, fluid flows out of front right and back right accumulators 442 a, 442 c and into the second rebound chamber 428 b of the front right damper 402 b, into the fourth rebound chamber 428 d of the back right damper 402 d, into the first compression chamber 426 a of the front left damper 402 a, and into the third compression chamber 426 c of the back left damper 402 c. The resulting pressure difference between the dampers 402 a, 402 b, 402 c, 402 d generates damper forces that counteract or resist the roll moment of the vehicle. Additional roll resistance can be added by opening the second manifold valve 422 b and the second manifold comfort valve 460 b as the bi-directional pump 410 is running in the first direction where the bi-directional pump 410 draws in hydraulic fluid from the reservoir hydraulic line 418 and discharges hydraulic fluid into the pump hydraulic line 408 to produce a positive pressure in the pump hydraulic line 408, which increases fluid pressure in the second and third hydraulic circuits 420 b, 420 c.

During braking, the momentum of the sprung weight of the vehicle tends to make the vehicle pitch or dive forward, compressing the front left damper 402 a and the front right damper 402 b. When this occurs, fluid flows out from the first compression chamber 426 a of the front left damper 402 a into the first cross-over hydraulic line 464 a and out from the second compression chamber 426 b of the front right damper 402 b into the second cross-over hydraulic line 464 b. As a result of the weight transfer to the front of the vehicle, the back left damper 402 c and back right damper 402 d begin to extend, causing fluid to flow out of the third rebound chamber 428 c of the back left damper 402 c into the second cross-over hydraulic line 464 b and out of the fourth rebound chamber 428 d of the back right damper 402 d into the first cross-over hydraulic line 464 a. With the front left, front right, back left, and back right comfort valves 444 a, 444 b, 444 c, 444 d and the first and second manifold comfort valves 460 a, 460 b all closed, the fluid flow out of the third rebound chamber 428 c of the back left damper 402 c and the fourth rebound chamber 428 d of the back right damper 402 d into the first and second cross-over hydraulic lines 464 a, 464 b increases the pressure in the front left and front right accumulators 442 a, 442 b, thus providing a passive pitch resistance where it becomes increasingly more difficult to compress the front left damper 402 a and the front right damper 402 b since the first compression chamber 426 a of the front left damper 402 a and the second compression chamber 426 b of the front right damper 402 b are connected in fluid communication with the first and second hydraulic circuits 420 a, 420 b.

During acceleration, the momentum of the sprung weight of the vehicle tends to make the vehicle pitch or squat rearward (i.e., aft), compressing the back left damper 402 c and the back right damper 402 d. When this occurs, fluid flows out from the third compression chamber 426 c of the back left damper 402 c into the fourth cross-over hydraulic line 464 d and out of the fourth compression chamber 426 d of the back right damper 402 d into the third cross-over hydraulic line 464 c. As a result of the weight transfer to the back/rear of the vehicle, the front left damper 402 a and front right damper 402 b begin to extend, causing fluid to flow out of the first rebound chamber 428 a of the front left damper 402 a into the third cross-over hydraulic line 464 c and out of the second rebound chamber 428 b of the front right damper 402 b into the fourth cross-over hydraulic line 464 d. With the front left, front right, back left, and back right comfort valves 444 a, 444 b, 444 c, 444 d and the first and second manifold comfort valves 460 a, 460 b all closed, the fluid flow out of the first rebound chamber 428 a of the front left damper 402 a and the second rebound chamber 428 b of the front right damper 402 b into the third and fourth cross-over hydraulic lines 464 c, 464 d increases the pressure in the back left and back right accumulators 442 c, 442 d, thus providing a passive pitch resistance where it becomes increasingly more difficult to compress the back left damper 402 c and the back right damper 402 d since the third compression chamber 426 c of the back left damper 402 c and the fourth compression chamber 426 d of the back right damper 402 d are connected in fluid communication with the third and fourth hydraulic circuits 420 c, 420 d.

When active or passive roll and/or pitch stiffness is not required, the four comfort valves 444 a, 444 b, 444 c, 444 d and the two manifold comfort valves 460 a, 460 b can be opened to enhance the ride comfort of the suspension system 400 and reduce or eliminate unwanted suspension movements resulting from the hydraulic coupling of one damper of the system to another damper of the system (e.g., where the compression of one damper causes movement and/or a dampening change in another damper). For example, when the front left comfort valve 444 a is open and the front left damper 402 a undergoes a compression stroke as the front wheel hits a bump, fluid may flow from the first compression chamber 426 a of the front left damper 402 a, into the first cross-over hydraulic line 464 a, from the first cross-over hydraulic line 464 a to the third cross-over hydraulic line 464 c by passing through the front left bridge hydraulic line 440 a and the front left comfort valve 444 a, and into the first rebound chamber 428 a of the front left damper 402 a. Thus, fluid can travel from the first compression chamber 426 a to the first rebound chamber 428 a of the front left damper 402 a with the only restriction coming from the dampening valves in the rebound and compression chamber ports 430 a, 430 b of the front left damper 402 a. As such, when all of the comfort valves 444 a, 444 b, 444 c, 444 d and the manifold comfort valves 460 a, 460 b are open, the dampers 402 a, 402 b, 402 c, 402 d are effectively decoupled from one another for improved ride comfort. It should also be appreciated that to return the suspension system 400 to this “comfort mode” of operation, the manifold valves 422 a, 422 b, 422 c, 422 d and/or the manifold comfort valves 460 a, 460 b may be opened while the bi-directional pump 410 is running in a second direction where the bi-directional pump 410 draws in hydraulic fluid from the pump hydraulic line 408 and discharges hydraulic fluid into the reservoir hydraulic line 418 to produce a negative pressure in the pump hydraulic line 408 that reduces fluid pressure in the hydraulic circuits 420 a, 420 b, 420 c, 420 d of the suspension system 400.

FIG. 5 illustrates the manifold assembly 404 of the suspension system 400 in more detail. The manifold assembly 404 includes first and second piston bores 466 a, 466 b that slidingly receive first and second floating pistons 468 a, 468 b, respectively. Each floating piston 468 a, 468 b includes a piston rod 458 and first and second piston heads 470 a, 470 b that are fixably coupled to opposing ends of the piston rod 458. A chamber divider 472 is fixably mounted at a midpoint of each of the first and second piston bores 466 a, 466 b. Each chamber divider 472 includes a through-bore that slidingly receives the piston rod 458. As such, the first piston bore 466 a is divided by the first floating piston 468 a into a first piston chamber 474 a that is arranged in fluid communication with the first manifold conduit 462 a, a second piston chamber 474 b disposed between the first piston head 470 a of the first floating piston 468 a and the chamber divider 472 in the first piston bore 466 a, a third piston chamber 474 c disposed between the second piston head 470 b of the first floating piston 468 a and the chamber divider 472 in the first piston bore 466 a, and a fourth piston chamber 474 d that is arranged in fluid communication with the fifth manifold conduit 462 e. Similarly, the second piston bore 466 b is divided by the second floating piston 468 b into a fifth piston chamber 474 e that is arranged in fluid communication with the second manifold conduit 462 b, a sixth piston chamber 474 f disposed between the first piston head 470 a of the second floating piston 468 b and the chamber divider 472 in the second piston bore 466 b, a seventh piston chamber 474 g disposed between the second piston head 470 b of the second floating piston 468 b and the chamber divider 472 in the second piston bore 466 b, and an eighth piston chamber 474 h that is arranged in fluid communication with the sixth manifold conduit 462 f. Optionally, biasing members (e.g., springs) (not shown) may be placed in the second, third, sixth, and seventh piston chambers 474 b, 474 c, 474 f, 474 g to naturally bias the first and second floating pistons 468 a, 468 b to a centered position where the second and third piston chambers 474 b, 474 c and the sixth and seventh piston chambers 474 f, 474 g have equal volumes.

The first manifold conduit 462 a is arranged in fluid communication with the first manifold hydraulic line 438 a, the second manifold conduit 462 b is arranged in fluid communication with the second manifold hydraulic line 438 b, the fifth manifold conduit 462 e is arranged in fluid communication with the fourth manifold hydraulic line 438 d, and the sixth manifold conduit 462 f is arranged in fluid communication with the third manifold hydraulic line 438 c. The third manifold conduit 462 c is arranged in fluid communication with the second and sixth piston chambers 474 b, 474 f while the fourth manifold conduit 462 d is arranged in fluid communication with the third and seventh piston chambers 474 c, 474 g. As a result, fluid pressure in the fourth piston chamber 474 d and thus the fifth manifold conduit 462 e can be increased independently of the first manifold conduit 462 a by closing the first manifold comfort valve 460 a and opening the fourth manifold valve 422 d when the bi-directional pump 410 is running in the first direction, which increases pressure in the third piston chamber 474 c and urges the first floating piston 468 a to the right in FIG. 5 , decreasing the volume of the fourth piston chamber 474 d and increasing the pressure in the fourth piston chamber 474 d. Similarly, fluid pressure in the eighth piston chamber 474 h and thus the sixth manifold conduit 462 f can be increased independently of the second manifold conduit 462 b by closing the second manifold comfort valve 460 b and opening the fourth manifold valve 422 d when the bi-directional pump 410 is running in the first direction, which increases pressure in the seventh piston chamber 474 g and urges the second floating piston 468 b to the right in FIG. 5 , decreasing the volume of the eighth piston chamber 474 h and increasing the pressure in the eighth piston chamber 474 h.

Fluid pressure in the first piston chamber 474 a and thus the first manifold conduit 462 a can also be increased without opening the first manifold valve 422 a by actuating the first floating piston 468 a, where the first manifold comfort valve 460 a is closed and the third manifold valve 422 c is open when the bi-directional pump 410 is running in the first direction, which increases pressure in the second piston chamber 474 b and urges the first floating piston 468 a to the left in FIG. 5 , decreasing the volume of the first piston chamber 474 a and increasing the pressure in the first piston chamber 474 a. Similarly, fluid pressure in the fifth piston chamber 474 e and the second manifold conduit 462 b can also be increased without opening the second manifold valve 422 b by actuating the second floating piston 468 b, where the second manifold comfort valve 460 b is closed and the third manifold valve 422 c is open when the bi-directional pump 410 is running in the first direction, which increases pressure in the sixth piston chamber 474 f and urges the second floating piston 468 b to the left in FIG. 5 , decreasing the volume of the fifth piston chamber 474 e and increasing the pressure in the second piston chamber 474 e.

The manifold assembly 404 may further include a first manifold accumulator 476 a that is arranged in fluid communication with the third manifold conduit 462 c between the third manifold valve 422 c and the second and sixth piston chambers 474 b, 474 f and a second manifold accumulator 476 b that is arranged in fluid communication with the fourth manifold conduit 462 d between the third and seventh piston chambers 474 c, 474 g. The first and second manifold accumulators 476 a, 476 b may be constructed in a number of different ways. For example and without limitation, the first and second manifold accumulators 476 a, 476 b may have accumulation chambers and pressurized gas chambers that are separated by floating pistons or flexible membranes. Under braking, fluid flow within the four hydraulic circuits generates a pressure difference between the first and second manifold accumulators 476 a, 476 b, which in turn causes an increase in pressure in the front left and front right accumulators 442 a, 442 b and provides a pitch stiffness that resists the compression of the front dampers 402 a, 402 b and rebound/extension of the back dampers 402 c, 402 d. Under acceleration, fluid flow within the four hydraulic circuits generates an opposite pressure difference between the first and second manifold accumulators 476 a, 476 b, which in turn causes an increase in pressure in the back left and back right accumulators 442 c, 442 d and provides a pitch stiffness that resists the rebound/extension of the front dampers 402 a, 402 b and compression of the back dampers 402 c, 402 d. Additional pitch resistance can be added before a braking or acceleration event by opening the third and fourth manifold valves 422 c, 422 d as the bi-directional pump 410 is running in the first direction. The bi-directional pump 410 draws in hydraulic fluid from the reservoir hydraulic line 418 and discharges hydraulic fluid into the pump hydraulic line 408 to produce a positive pressure in the pump hydraulic line 408, which increases fluid pressure in the first and second manifold accumulators 476 a, 476 b. In a similar way, the pitch stiffness of the system can be reduced before a braking or acceleration event by running the bi-directional pump 410 in the second direction while the third and fourth manifold valves 422 c, 422 d.

The manifold assembly 404 may also include six pressure sensors 424 a, 424 b, 424 c, 424 d, 424 e, 424 f: a first pressure sensor 424 a arranged to monitor fluid pressure in the first manifold conduit 462 a, a second pressure sensor 424 b arranged to monitor fluid pressure in the second manifold conduit 462 b, a third pressure sensor 424 c arranged to monitor fluid pressure in the third manifold conduit 462 c, a fourth pressure sensor 424 d arranged to monitor fluid pressure in the fourth manifold conduit 462 d, a fifth pressure sensor 424 e arranged to monitor fluid pressure in the fifth manifold conduit 462 e, and a sixth pressure sensor 424 f arranged to monitor fluid pressure in the sixth manifold conduit 462 f. While not shown in FIG. 5 , the pressure sensors 424 a, 424 b, 424 c, 424 d, 424 e, 424 f are all electrically connected to the suspension control module 123.

FIG. 6 illustrates another suspension system 600 that shares many of the same components as the suspension system 400 illustrated in FIGS. 4 and 5 , but in FIG. 6 different pump 610 and manifold assemblies 604 have been utilized. Rather than repeat the description set forth above, the following paragraphs describe the structure and function of the components in FIG. 6 that are new and/or different from those shown and described in connection with FIGS. 4 and 5 . It should be appreciated that the reference numbers in FIGS. 4 and 5 are “400” series numbers (e.g., 400, 402, 404, etc.) whereas the components in FIG. 6 that are the same or similar to the components of the suspension system 400 shown in FIGS. 4 and 5 share the same base reference numbers, but are listed as “600” series numbers (e.g., 600, 602, 604, etc.). Thus, the same description for element 400 above applies to element 600 in FIG. 6 and so on and so forth.

The pump assembly 606 illustrated in FIG. 6 includes a single direction pump 610 with an inlet port that is connected in fluid communication with the hydraulic reservoir 612 by a reservoir hydraulic line 618 and an outlet port that is connected to the pump hydraulic line 608. In operation, the single direction pump 610 draws in hydraulic fluid from the reservoir hydraulic line 618 via the inlet port and discharges hydraulic fluid into the pump hydraulic line 608 via the outlet port. As such, the single direction pump 610 produces a positive pressure in the pump hydraulic line 608 that can be used by manifold assembly 604 to increase fluid pressure in the suspension system 600. A check valve 678 is positioned in the pump hydraulic line 608 to prevent back feed when the single direction pump 610 is turned off. The pump assembly 606 also includes a return hydraulic line 680 that extends from the pump hydraulic line 108 to the hydraulic reservoir 612. A first pump valve 682 a is positioned in-line with the return hydraulic line 680. The pump assembly 606 also includes a pump bridge hydraulic line 683 that includes a second pump valve 682 b mounted in-line with the pump bridge hydraulic line 683. The pump bridge hydraulic line 683 connects to the pump hydraulic line 608 at a location between the single direct pump 610 and the check valve 678 and connects to the return hydraulic line 680 at a location between the first pump valve 682 a and the hydraulic reservoir 612. In accordance with this arrangement, fluid pressure in the pump hydraulic line 608 can be increased by turning on the pump 610 and closing the second pump valve 682 b and fluid pressure in the pump hydraulic line 608 can be decreased by turning the pump 610 off and opening the first pump valve 682 a.

In the example illustrated in FIG. 6 , only three manifold valves 622 a, 622 b, 622 c (i.e., the first manifold valve 622 a, the second manifold valve 622 b, and the third manifold valve 622 c) are connected in parallel with the pump hydraulic line 608. The fourth manifold valve 622 d is positioned between the first and second piston bores 666 a, 666 b and is arranged in fluid communication with the third manifold conduit 662 c on one side and the fourth manifold conduit 662 d on the other side. Thus, to increase fluid pressure in the fifth and/or sixth manifold conduits 662 e, 662 f independently of the first and second manifold conduits 662 a, 662 b, the third and fourth manifold valves 622 c, 622 d must be open while the pump 610 is running and the first and second manifold comfort valves 660 a, 660 b are closed to increase fluid pressure in the third and seventh piston chambers 674 c, 674 g, which urges the first and second floating pistons 668 a, 668 b to the right in FIG. 6 decreasing the volume of the fourth and eighth piston chambers 674 d, 674 h and increasing the pressure in the fourth and eighth piston chambers 674 d, 674 h.

FIG. 7 illustrates another suspension system 700 that shares many of the same components as the suspension system 400 illustrated in FIGS. 4 and 5 , but in FIG. 7 a different manifold assembly 704 has been utilized. Rather than repeat the description set forth above, the following paragraphs describe the structure and function of the components in FIG. 7 that are new and/or different from those shown and described in connection with FIGS. 4 and 5 . It should be appreciated that the reference numbers in FIGS. 4 and 5 are “400” series numbers (e.g., 400, 402, 404, etc.) whereas the components in FIG. 7 that are the same or similar to the components of the suspension system 400 shown in FIGS. 4 and 5 share the same base reference numbers, but are listed as “700” series numbers (e.g., 700, 702, 704, etc.). Thus, the same description for element 400 above applies to element 700 in FIG. 7 and so on and so forth.

The manifold assembly 704 illustrated in FIG. 7 has the same components and hydraulic arrangement as the manifold assembly 404 illustrated in FIGS. 4 and 5 , but in FIG. 7 the placement of the various components of the manifold assembly 704 is different to allow the manifold assembly 704 to be packaged in the front of the vehicle between the front dampers 702 a, 702 b. The manifold assembly 704 illustrated in FIG. 7 includes a front left sub-assembly 784 a and a front right sub-assembly 784 b. The front right sub-assembly 784 b includes the first piston bore 766 a, the first floating piston 768 a, the first manifold valve 722 a, the third manifold valve 722 c, the first manifold conduit 762 a, and the fifth manifold conduit 762 e. The front left sub-assembly 784 a includes the second piston bore 466 b, the second floating piston 768 b, the second manifold valve 722 b, the fourth manifold valve 722 d, the second manifold conduit 762 b, and the sixth manifold conduit 762 f. The pump hydraulic line 708 extends between the front left and front right sub-assemblies 784 a, 784 b and splits to connect to the manifold valves 722 a, 722 b, 722 c, 722 d on either side. The third and fourth manifold conduits 762 c, 762 d extend laterally between the front left and front right sub-assemblies 784 a, 784 b to connect the second and sixth piston chambers 774 b, 774 f and the third and seventh piston chambers 774 c, 774 g, respectively. It should be appreciated that the order and arrangement of the piston chambers 774 e, 774 f, 774 g, 774 h in the second piston bore 766 b shown in FIG. 7 is opposite from that shown in FIGS. 4 and 5 . In other words, in accordance with the arrangement shown in FIG. 7 , the first piston chamber 774 a (which is connected in fluid communication with the first manifold conduit 762 a) faces the fifth piston chamber 774 e (which is connection in fluid communication with the second manifold conduit 762 b). In other words, in FIG. 7 the fifth piston chamber 774 e (which is connection in fluid communication with the second manifold conduit 762 b) is to the right of the eighth piston chamber 774 h (which is connected in fluid communication with the sixth manifold conduit 762 f), whereas in FIGS. 4 and 5 the fifth piston chamber 474 e (which is connected in fluid communication with the second manifold conduit 462 b) is to the left of the eighth piston chamber 474 h (which is connected in fluid communication with the sixth manifold conduit 462 f). This reversal of the arrangement of the piston chambers 774 e, 774 f, 774 g, 774 h in the second piston bore 766 b simplifies and shortens the runs required for the manifold hydraulic lines 738 a, 738 b, 738 c, 738 d and is therefore advantageous.

FIG. 8 includes a functional block diagram of an example implementation of the suspension control module 123. A pump control module 804 receives power from a battery 808 of the vehicle. The pump control module 804 controls operation, speed, and direction of operation of a pump 812 of the suspension system. More specifically, the pump control module 804 controls application of power to the pump 812 of the suspension system. Examples of the pump 812 are discussed above. For example, in the examples of FIGS. 1-4 , the pump control module 804 controls application of power to the pump 110, 210, 310, or 410. In the examples of FIGS. 6 and 7 , the pump control module 804 controls application of power to the pump 610 or 710. The pump control module 804 may control, for example, a polarity of power applied to the pump 812, a frequency of power applied to the pump 812, a magnitude of voltage applied to the pump 812, and/or a current through the pump 812.

A valve control module 816 controls actuation (e.g., opening and closing) of valves 820 of the suspension system. Examples of the valves 820 are discussed above with respect to examples of FIGS. 1-7 . For example, the valve control module 816 controls actuation of the valves 122 a, 122 b, 144 a-c, and 146 a-b in the example of FIG. 1 . The present application is also applicable to the other FIGS. 2-7 .

Referring back to FIG. 1 , the tank 112 may be not accessible to add hydraulic fluid into the suspension system or to remove hydraulic fluid from the system. The tank 112 may not include a port, opening, inlet, nozzle, etc. through which hydraulic fluid can be externally input to the tank 112 or externally removed from the tank 112.

As such, the suspension system may include a quick connect valve 160. The quick connect valve 160 may be fluidly connected, for example, to the line 132 a or in another suitable location. While the quick connect valve 160 is shown in the example of FIG. 1 , the quick connect valve 160 can be included in all of the suspension systems above and the following is also applicable to all of the example embodiments shown and described. In various implementations, two or more quick connect valves may be included.

An external pump can be connected to the quick connect valve 160 via a hydraulic line, such as to fill the suspension system with hydraulic fluid and/or to pump hydraulic fluid out of the suspension system. In various implementations, the pump 812 may be used to pump hydraulic fluid out of the suspension system.

A service module 176 may control operation of the external pump and performance of one or more operations. The service module 176 may, for example, connect to an on board diagnostic (OBD) port of the vehicle. Via the OBD port, the service module 176 may coordinate control of various components with the suspension control module 123, receive one or more operating parameters (e.g., pressures measured by the pressure sensors discussed above), and perform one or more other functions. For example, the service module 176 may communicate with the suspension control module 123 to perform to determine whether a fault is present in one or more of accumulators 832. This may be referred to as an accumulator check. The accumulators 832 may be the accumulators 142 a-d of FIG. 1 , the accumulators 242 a-d of FIG. 2 , the accumulators 342 a-d of FIG. 3 , the accumulators 442 a-d and the other accumulators of FIG. 4 , the accumulators 476 a-b of FIG. 5 , the accumulators 642 a-d and the other accumulators of FIG. 6 , and the accumulators 742 a-d and the other accumulators of FIG. 7 .

Referring back to FIG. 8 , a communication module 824 may communicate with the service module 176 using a communication protocol, such as a car area network (CAN) bus communication protocol or another suitable communication protocol.

An accumulator check module 828 controls operation of the pump 812 and actuation of the valves 820 to perform the accumulator check and to diagnose a fault in one or more of the accumulators 832. For example, the accumulator check module 828 may determine whether the accumulators 832 all have sufficient pressure.

The accumulator check is performed using the pressures measured by pressure sensors 840, such as the pressure sensors 124 a-b in the example of FIG. 1 , the pressure sensors 224 a-c in the example of FIG. 2 , the pressure sensors 324 a-d in the example of FIG. 3 , or the pressure sensors of the examples of FIG. 4, 5, 6 , or 7.

FIG. 9 is a functional block diagram of an example implementation of the accumulator check module 828. A command module 904 generates commands for operation of the pump 812 and actuation of the valves 820 for the accumulator check. The pump control module 804 controls the pump 812 according to the pump command, and the valve control module 816 actuates the valves 820 according to the valve command. In this manner, the accumulator check module 828 controls the pump 812 and the valves 820 for the accumulator check.

The command module 904 may start the leak check in response to receipt of a start signal, such as from the service module 176. The service module 176 may generate the start signal, for example, in response to receipt of user input indicative of a request to perform the accumulator check or in response to another event, such as the suspension system being filled, serviced, or diagnosed.

The command module 904 controls actuation of the valves 820 according to a present state of the accumulator check set by a state module 908 using a state table 912. The state table 912 includes target open/closed states of the valves 820, respectively, for each state of the accumulator check. The state module 908 proceeds through the states in a predetermined order, such as from a first state to a last state. For example, in the example of FIG. 4 , the front left corner accumulator may be checked first, the front right corner accumulator may be checked second, the rear right corner accumulator may be checked third, the rear left accumulator may be checked fourth, the front circuit may be checked fifth, and the rear circuit may be checked sixth. The valves 820 are actuated to allow the accumulators 832 to be diagnosed for a fault individually or in combinations of two or more.

A diagnosis module 916 monitors one of the pressures during each state and determines whether a fault is present in an accumulator based on the monitored pressure, as discussed further below. The diagnosis module 916 determines which pressure to monitor based on the present state of the accumulator check using the state table 912. Which pressure to monitor for each state may also be stored in the state table 912.

The diagnosis module 916 may store indicators in memory 920 based on the accumulator check. The indicators indicate whether the accumulators 832, respectively, have a fault. For example, the diagnosis module 916 may set an indicator associated with one of the accumulators 832 to a first state when the diagnosis module 916 determines that no fault is present in that one of the accumulators 832. The diagnosis module 916 may set the indicator associated with one of the accumulators 832 to a second state when the diagnosis module 916 determines that a fault is present in that one of the accumulators 832. The diagnosis module 916 may store an indicator in the memory 920 for each of the accumulators 832.

An indicator module 924 indicates (e.g., to the service module 176) whether the accumulators 832 have a fault or not based on the indicators in the memory 920. The indicator module 924 may take one or more actions when one or more of the accumulators 832 has a leak. For example, the indicator module 924 may transmit the indicators to the service module 176 for display on a display of the service module 176. One or more other actions may additionally or alternatively be taken when one or more of the accumulators 832 has a fault. For example, hydraulic fluid may be added to the suspension system, an accumulator with a fault may be replaced, etc.

FIGS. 10A and 10B are together a flowchart depicting an example method of performing the accumulator check and determining whether one or more of the accumulators 832 have a fault. Control begins with 1004, such as when the start signal is received.

At 1004, the state module 908 sets a present state (N) equal to 1. One or more accumulators is/are checked for each state. A total number of states may be equal to the number of accumulators. The total number of states may be greater than the number of accumulators in some implementations.

At 1008, the command module 904 determines how to actuate each of the valves 820 based on the present state N using the state table 912 and actuates (opens and closes) the valves 820 as defined in the state table 912 for the present state N. The diagnosis module 916 also determines which one of the pressures to monitor for the present state N using the state table 912 based on the present state N.

At 1008, the command module 904 also operates the pump 812 in the first direction to pump hydraulic fluid into the suspension system and increase pressure within a portion (circuit) of the suspension system. The valves are actuated to pressurize only one portion of the suspension systems (to which only one or two accumulators are connected) during each state.

At 1012, the diagnosis module 916 determines whether the pressure to monitor for the present state N is greater than or equal to a first predetermined pressure. The first predetermined pressure may be calibrated and may be, for example, approximately 20 bar or another suitable pressure. If 1012 is true, control continues with 1016. If 1012 is false, control may remain at 1012 and continue operating the pump 812 in the first direction.

At 1016, the command module 904 stops the pump 812 (e.g., stops applying power) and waits for a predetermined period. This allows the pressure being monitored to stabilize. At 1020, the command module 904 may open the seat valve(s) of the suspension system, such as 422 a and 422 b, to dump hydraulic fluid into the tank (e.g., 412) from the suspension system.

At 1024, the diagnosis module 916 monitors the second derivative of the pressure being monitored. For example, the diagnosis module 916 may determine the second derivative (d²x/dt² mathematically) or an approximation of the second order derivative, such as by applying a Savitkzy Golay filter. The Savitkzy Golay filter may determine the second derivative by fitting a second order polynomial to a predetermined number of measured pressure samples, such as 100 or 50 pressure samples, taken over time. The polynomial equation may be written as

P=at ² +bt+c,

where P is a pressure measured at a time t, and a, b, and c are coefficients fit to the predetermined number of measured pressures. The diagnosis module 916 may determine the second derivative (d²x/dt²) using the equation

$\frac{d^{2}x}{{dt}^{2}} = {{2a}.}$

FIG. 11 includes a top graph of example pressure over time and a bottom graph of example second derivative of pressure over time.

At 1028, the diagnosis module 916 determines whether the second derivative of pressure is greater than a predetermined value. The predetermined value is greater than zero and is calibrated, such as to approximately 40 or another suitable value, such as illustrated in the bottom graph of FIG. 11 . A knee is present in the pressure when the second derivative is greater than the predetermined value. Example knees are illustrated on the pressure and the second derivative by stars in FIG. 11 . If 1028 is true, control transfers to 1032. If 1028 is false, control continues with 1036. At 1032, the diagnosis module 916 stores the pressure at the knee point as a pre-charge pressure for the present test N, and control continues with 1036.

At 1036, the diagnosis module 916 determines whether the pressure being monitored is less than a second predetermined pressure that is less than the first predetermined pressure. The second predetermined pressure may be, for example, approximately 10 bar or 15 bar or another suitable pressure.

At 1040, the command module 904 closes the seat valves, such as 422 a and 422 b, to stop dumping the hydraulic fluid to the tank and waits for a predetermined period. This allows the pressure(s) being monitored to stabilize.

At 1044, the command module 904 also operates the pump 812 in the first direction to pump hydraulic fluid into the suspension system and increase pressure within the same portion of the suspension system. At 1048, the diagnosis module 916 determines whether the monitored pressure is greater than the first predetermined pressure (1 Predetermined Pressure in FIG. 10A) plus a predetermined amount (e.g., 2 bar or another suitable pressure). If 1048 is true, control transfers to 1052 of FIG. 10B. If 1048 is false, control returns to 1044 and continues increasing the monitored pressure.

Referring now to FIG. 10B, at 1052, the diagnosis module 916 stores the present value of the monitored pressure as a low pressure for the present test N, and the command module 904 continues to operate the pump 812 in the first direction to continue increasing the monitored pressure.

At 1056, the diagnosis module 916 determines a volumetric flowrate of the pump 812 while the pump 812 is operating in the first direction. The diagnosis module 916 may determine the volumetric flow rate, for example, based on the monitored pressure, a voltage applied to an electric motor of the pump 812, a current of the motor of the pump 812, and a temperature of the motor of the pump 812. A temperature sensor may measure the temperature of the motor. A current sensor may measure the current of the motor. A voltage sensor may measure the voltage of the electric motor. The diagnosis module 916 may determine the volumetric flow rate using one of an equation and a lookup table that relates pressures, currents, temperatures, and voltages to volumetric flow rates.

The diagnosis module 916 also determines a volume of hydraulic fluid input to the suspension system based on the volumetric flow rate at 1056. The diagnosis module 916 may, for example, determine the volume by determining a mathematical integral of the volumetric flowrate. The diagnosis module 916 also updates a total volume (of hydraulic fluid) input to the suspension system since the low pressure was recorded at 1056. The diagnosis module 916 may, for example, add the volume (determined by integrating the volumetric flow rate) to a previous value of the total volume input to update the total volume input. The total volume input therefore increases over time as hydraulic fluid is pumped into the suspension system.

At 1060, the diagnosis module 916 determines whether the monitored pressure is greater than a third predetermined pressure that is greater than the first predetermined pressure plus the predetermined amount. The third predetermined pressure may be calibrated and may be, for example, approximately 30 bar or another suitable pressure.

At 1064, the diagnosis module 916 stores the total volume input for the test N and the pressure at the time that the monitored pressure became greater than or equal to the third predetermined pressure. At 1068, the diagnosis module 916 diagnoses whether one or more faults are present in the accumulator of the portion of the suspension system based on the pre-charge pressure (from 1032) and the total volume input (from 1064). For example, the diagnosis module 916 may diagnose a fault in the accumulator when the pre-charge pressure is less than a predetermined pressure. The predetermined pressure is less than the first predetermined pressure and greater than or equal to the second predetermined pressure. The diagnosis module 916 may also store a fault when no pre-charge pressure is stored (e.g., when the pressure becomes less than or equal to the second predetermined pressure at 1036 before the second derivative becomes greater than the predetermined value at 1028). As another example, the diagnosis module 916 may diagnose a fault in the accumulator when the total volume input is less than a predetermined volume, such as 1 liter or another suitable volume.

At 1072, the state module 908 determines whether the present state (N) is equal to the total number of states of the accumulator check (e.g., 6 or another suitable number). If 1072 is false, the state module 908 increments the present state N (e.g., sets N=N+1) at 1076, and control returns to 1008 of FIG. 10A. If 1072 is false, control continues with 1080. At 1080, the indicator module 924 transmits the diagnoses of the accumulators to the service module 176, and control may end. One or more other actions may also be taken at 1080, such as displaying the diagnoses of the accumulators, respectively, on the display of the service module 176.

The foregoing description is merely illustrative in nature and is in no way intended to limit the disclosure, its application, or uses. The broad teachings of the disclosure can be implemented in a variety of forms. Therefore, while this disclosure includes particular examples, the true scope of the disclosure should not be so limited since other modifications will become apparent upon a study of the drawings, the specification, and the following claims. It should be understood that one or more steps within a method may be executed in different order (or concurrently) without altering the principles of the present disclosure. Further, although each of the embodiments is described above as having certain features, any one or more of those features described with respect to any embodiment of the disclosure can be implemented in and/or combined with features of any of the other embodiments, even if that combination is not explicitly described. In other words, the described embodiments are not mutually exclusive, and permutations of one or more embodiments with one another remain within the scope of this disclosure.

Spatial and functional relationships between elements (for example, between modules, circuit elements, semiconductor layers, etc.) are described using various terms, including “connected,” “engaged,” “coupled,” “adjacent,” “next to,” “on top of,” “above,” “below,” and “disposed.” Unless explicitly described as being “direct,” when a relationship between first and second elements is described in the above disclosure, that relationship can be a direct relationship where no other intervening elements are present between the first and second elements, but can also be an indirect relationship where one or more intervening elements are present (either spatially or functionally) between the first and second elements. As used herein, the phrase at least one of A, B, and C should be construed to mean a logical (A OR B OR C), using a non-exclusive logical OR, and should not be construed to mean “at least one of A, at least one of B, and at least one of C.”

In the figures, the direction of an arrow, as indicated by the arrowhead, generally demonstrates the flow of information (such as data or instructions) that is of interest to the illustration. For example, when element A and element B exchange a variety of information but information transmitted from element A to element B is relevant to the illustration, the arrow may point from element A to element B. This unidirectional arrow does not imply that no other information is transmitted from element B to element A. Further, for information sent from element A to element B, element B may send requests for, or receipt acknowledgements of, the information to element A.

In this application, including the definitions below, the term “module” or the term “controller” may be replaced with the term “circuit.” The term “module” may refer to, be part of, or include: an Application Specific Integrated Circuit (ASIC); a digital, analog, or mixed analog/digital discrete circuit; a digital, analog, or mixed analog/digital integrated circuit; a combinational logic circuit; a field programmable gate array (FPGA); a processor circuit (shared, dedicated, or group) that executes code; a memory circuit (shared, dedicated, or group) that stores code executed by the processor circuit; other suitable hardware components that provide the described functionality; or a combination of some or all of the above, such as in a system-on-chip.

The module may include one or more interface circuits. In some examples, the interface circuits may include wired or wireless interfaces that are connected to a local area network (LAN), the Internet, a wide area network (WAN), or combinations thereof. The functionality of any given module of the present disclosure may be distributed among multiple modules that are connected via interface circuits. For example, multiple modules may allow load balancing. In a further example, a server (also known as remote, or cloud) module may accomplish some functionality on behalf of a client module.

The term code, as used above, may include software, firmware, and/or microcode, and may refer to programs, routines, functions, classes, data structures, and/or objects. The term shared processor circuit encompasses a single processor circuit that executes some or all code from multiple modules. The term group processor circuit encompasses a processor circuit that, in combination with additional processor circuits, executes some or all code from one or more modules. References to multiple processor circuits encompass multiple processor circuits on discrete dies, multiple processor circuits on a single die, multiple cores of a single processor circuit, multiple threads of a single processor circuit, or a combination of the above. The term shared memory circuit encompasses a single memory circuit that stores some or all code from multiple modules. The term group memory circuit encompasses a memory circuit that, in combination with additional memories, stores some or all code from one or more modules.

The term memory circuit is a subset of the term computer-readable medium. The term computer-readable medium, as used herein, does not encompass transitory electrical or electromagnetic signals propagating through a medium (such as on a carrier wave); the term computer-readable medium may therefore be considered tangible and non-transitory. Non-limiting examples of a non-transitory, tangible computer-readable medium are nonvolatile memory circuits (such as a flash memory circuit, an erasable programmable read-only memory circuit, or a mask read-only memory circuit), volatile memory circuits (such as a static random access memory circuit or a dynamic random access memory circuit), magnetic storage media (such as an analog or digital magnetic tape or a hard disk drive), and optical storage media (such as a CD, a DVD, or a Blu-ray Disc).

The apparatuses and methods described in this application may be partially or fully implemented by a special purpose computer created by configuring a general purpose computer to execute one or more particular functions embodied in computer programs. The functional blocks, flowchart components, and other elements described above serve as software specifications, which can be translated into the computer programs by the routine work of a skilled technician or programmer.

The computer programs include processor-executable instructions that are stored on at least one non-transitory, tangible computer-readable medium. The computer programs may also include or rely on stored data. The computer programs may encompass a basic input/output system (BIOS) that interacts with hardware of the special purpose computer, device drivers that interact with particular devices of the special purpose computer, one or more operating systems, user applications, background services, background applications, etc.

The computer programs may include: (i) descriptive text to be parsed, such as HTML (hypertext markup language), XML (extensible markup language), or JSON (JavaScript Object Notation) (ii) assembly code, (iii) object code generated from source code by a compiler, (iv) source code for execution by an interpreter, (v) source code for compilation and execution by a just-in-time compiler, etc. As examples only, source code may be written using syntax from languages including C, C++, C#, Objective-C, Swift, Haskell, Go, SQL, R, Lisp, Java®, Fortran, Perl, Pascal, Curl, OCaml, Javascript®, HTML5 (Hypertext Markup Language 5th revision), Ada, ASP (Active Server Pages), PHP (PHP: Hypertext Preprocessor), Scala, Eiffel, Smalltalk, Erlang, Ruby, Flash®, Visual Basic®, Lua, MATLAB, SIMULINK, and Python®. 

What is claimed is:
 1. An accumulator checking system for a suspension system of a vehicle, the accumulator checking system comprising: a state module configured to selectively set a present state of an accumulator check for the suspension system to a first state; a valve control module configured to determine first target open and closed states for valves of the suspension system based on the present state being set to the first state and to open and close the valves of the suspension system according to the first target open and closed states, respectively; a pump control module configured to, when the valves are in the first target open and closed states, respectively, selectively operate an electric pump of the suspension system in a first direction and increase a pressure of hydraulic fluid in a first portion of the suspension system including an accumulator, wherein the valve control module is configured to selectively open one or more of the valves to decrease the pressure in the first portion after the increase; and a diagnosis module configured to: selectively record the pressure in the first portion based on a second derivative of the pressure while the pressure is decreasing; and selectively diagnose a fault in the accumulator based on the recorded pressure.
 2. The accumulator check system of claim 1 wherein the diagnosis module is configured to record the pressure in the first portion when the second derivative of the pressure is greater than a predetermined value.
 3. The accumulator check system of claim 1 wherein the diagnosis module is configured to determine the second derivative of the pressure in the first portion.
 4. The accumulator check system of claim 3 wherein the diagnosis module is configured to determine the second derivative of the pressure using a Savitzky Golay filter.
 5. The accumulator check system of claim 1 wherein the diagnosis module is configured to diagnose the fault in the accumulator when the recorded pressure is less than a predetermined pressure.
 6. The accumulator check system of claim 5 wherein the diagnosis module is configured to selectively diagnose that no fault is present in the accumulator when the recorded pressure is greater than the predetermined pressure.
 7. The accumulator check system of claim 1 wherein the diagnosis module is further configured to: determine a total volume of hydraulic fluid input to the first portion of the suspension system while the pump control module operated the electric pump in the first direction and increased the pressure from a first predetermined pressure to a second predetermined pressure; and selectively diagnose the fault in the accumulator further based on the total volume of hydraulic fluid input.
 8. The accumulator check system of claim 7 wherein the diagnosis module is configured to diagnose the fault when the total volume of hydraulic fluid input to the first portion is less than a predetermined volume.
 9. The accumulator check system of claim 8 wherein the diagnosis module is configured to diagnose that no fault is present in the accumulator when the total volume of hydraulic fluid input to the first portion is greater than the predetermined volume.
 10. The accumulator check system of claim 1 wherein: the state module is configured to selectively set the present state of the accumulator check for the suspension system to a second state; the valve control module is configured to determine second target open and closed states for the valves of the suspension system based on the present state being set to the second state and to open and close the valves of the suspension system according to the second target open and closed states, respectively; the pump control module is configured to, when the valves are in the second target open and closed states, respectively, selectively operate the electric pump of the suspension system in the first direction and increase a second pressure of hydraulic fluid in a second portion of the suspension system including a second accumulator, the valve control module is configured to selectively open one or more of the valves to decrease the second pressure in the second portion after the increase in the second portion; and the diagnosis module configured to: selectively record the second pressure in the second portion based on a second derivative of the second pressure; and selectively diagnose a fault in the second accumulator based on the recorded second pressure.
 11. An accumulator checking system for a suspension system of a vehicle, the accumulator checking system comprising: a state module configured to selectively set a present state of an accumulator check for the suspension system to a first state; a valve module configured to determine first target open and closed states for valves of the suspension system based on the present state being set to the first state and to open and close the valves of the suspension system according to the first target open and closed states, respectively; a pump control module configured to, when the valves are in the first target open and closed states, respectively, selectively operate an electric pump of the suspension system in a first direction and increase a pressure of hydraulic fluid in a first portion of the suspension system including an accumulator; and a diagnosis module configured to: determine a total volume of hydraulic fluid input to the first portion of the suspension system while the pump control module operated the electric pump in the first direction and increased the pressure from a first predetermined pressure to a second predetermined pressure; and selectively diagnose the fault in the accumulator based on the total volume of hydraulic fluid input to the first portion.
 12. An accumulator checking method for a suspension system of a vehicle, the accumulator checking method comprising: selectively setting a present state of an accumulator check for the suspension system to a first state; determining first target open and closed states for valves of the suspension system based on the present state being set to the first state; selectively opening and closing the valves of the suspension system according to the first target open and closed states, respectively; when the valves are in the first target open and closed states, respectively, selectively operating an electric pump of the suspension system in a first direction and increasing a pressure of hydraulic fluid in a first portion of the suspension system including an accumulator; selectively opening one or more of the valves and decreasing the pressure in the first portion after the increasing; selectively recording the pressure in the first portion based on a second derivative of the pressure while the pressure is decreasing; and selectively diagnosing a fault in the accumulator based on the recorded pressure.
 13. The accumulator check method of claim 12 wherein selectively recording includes recording the pressure in the first portion when the second derivative of the pressure is greater than a predetermined value.
 14. The accumulator check method of claim 12 further comprising determining the second derivative of the pressure in the first portion.
 15. The accumulator check method of claim 14 wherein determining the second derivative includes determining the second derivative of the pressure using a Savitzky Golay filter.
 16. The accumulator check method of claim 12 wherein selectively diagnosing a fault includes diagnosing the fault in the accumulator when the recorded pressure is less than a predetermined pressure.
 17. The accumulator check method of claim 16 wherein selectively diagnosing a fault includes diagnosing that no fault is present in the accumulator when the recorded pressure is greater than the predetermined pressure.
 18. The accumulator check method of claim 12 further comprising: determining a total volume of hydraulic fluid input to the first portion of the suspension system while the pump control module operated the electric pump in the first direction and increased the pressure from a first predetermined pressure to a second predetermined pressure, wherein selectively diagnosing a fault includes diagnosing the fault in the accumulator further based on the total volume of hydraulic fluid input.
 19. The accumulator check method of claim 18 wherein selectively diagnosing a fault includes diagnosing the fault when the total volume of hydraulic fluid input to the first portion is less than a predetermined volume.
 20. The accumulator check method of claim 19 wherein selectively diagnosing a fault includes diagnosing that no fault is present in the accumulator when the total volume of hydraulic fluid input to the first portion is greater than the predetermined volume. 